CN86108430A - The method and apparatus that is used for testing vehicles - Google Patents
The method and apparatus that is used for testing vehicles Download PDFInfo
- Publication number
- CN86108430A CN86108430A CN198686108430A CN86108430A CN86108430A CN 86108430 A CN86108430 A CN 86108430A CN 198686108430 A CN198686108430 A CN 198686108430A CN 86108430 A CN86108430 A CN 86108430A CN 86108430 A CN86108430 A CN 86108430A
- Authority
- CN
- China
- Prior art keywords
- wheel
- automobile
- base
- vibration
- spring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
- G01M17/04—Suspension or damping
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Vehicle Body Suspensions (AREA)
- Automobile Manufacture Line, Endless Track Vehicle, Trailer (AREA)
- Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)
Abstract
A kind of method of checking the automobile chassis state.The free-falling from the bracing frame of the propons of automobile and back axle can be measured the wheel pressure that acts on the base on a base.The maximum height that falls is corresponding with the distance between axletree and the fixed stop absorber.Wheel falls under spring force effect lax between vehicle gravity and vehicle body and the wheel, and the speed that bracing frame removes is consistent with the speed that wheel falls at least.A device of carrying out this method comprises a movably vehicle bracing frame, and it is positioned on the base of a measurement bridge-type.
Description
The present invention relates to an a kind of method of state of testing vehicles and a device implementing this method.Automobile is placed on the positioning supporting frame of base top, then this positioning supporting frame is removed.
As everyone knows, in order to evaluate the roadworthiness of an automobile, people wish to check the state in vibration damper, suspension and the axle joint of automobile.
In actual applications, check that the method in common of the defective of a vibration damper is use hand electrical automobile, according to the state of the vibration characteristics judgement vibration damper of automobile.This is the method for a pure subjectivity, and it depends on mechanician's experience, and can not get the requirement on any precision.
Proposed a test method, this method can be made comparisons the state of the state of tested vibration damper and satisfactory vibration damper.
In this test method, automobile is driven on the overhead bracing frame above the platform, and after the locking device of bracing frame was untied, automobile fell, and its drop is the distance between platform and the ground.Meanwhile, vehicle body is energized and vibrates, and the vibration processes of vehicle body is just noted by connection lever measuring mechanism onboard.Utilize this method, can simulate in test the vibration characteristics of vehicle body under various pavement conditions, therefore can obtain the best information of relevant vehicle running smoothness aspect authenticity.But in this case, the information of relevant vibration-damper characterist but can only obtain indirectly, because the vibration processes of record can only be made comparisons with the data of the satisfactory vibration damper of form compilation with vibration damper factory.Therefore, this method is not suitable for the virtual condition of estimating vibration damper, can not provide the fully accurate information of vibration damper state.
In actual applications, said method is not suitable for the vibration damper of evaluation independent suspension automobile.In vehicle free-falling process, because wheel is with respect to the resilience of vehicle body, wheel institute warp be an arcuate path, the track of this route can be determined as radius with the wheel shaft that links to each other with the joint, so, wheel is to depart from colliding surface on the position of vertical plane, and this has just produced suitable interference to spring system, so that vibration has been freely no longer.Therefore, utilizing this method is the actual vibration characteristic of automobile in can not the dry run process, and for qualification test result correctly, needs the actual vibration characteristic of simulated automotive correctly again.
In addition, compare with the vibration of vehicle body, this known test method can not be made difference between the vibration characteristics of the damping characteristic in the characteristic of vibration damper, axle joint and wheel.Or rather, it can only provide the symphyogenetic general information of above-mentioned all vibration effect factors, that is resembles noted earlierly, and a general estimation of vehicle running smoothness is provided.Because the vibration-damper characterist that is reflected in the test findings only accounts for minimum ratio, therefore obtaining this estimation can not correctly estimate vehicle shock absorber.In addition, in method described above, owing to load in the automobile and the interior oil of its fuel tank are included in the test findings, so the reliability of this evaluation just more becomes a problem.
The objective of the invention is to propose one can be under the condition similar to the operation characteristic of automobile, the method that state, axle joint feature and the unsteadiness of wheels characteristic of vibration damper detected individually, and the device of implementing this method is provided.
According to this invention, as described in the article beginning, in the method:
1. the distance between positioning supporting frame and the base is equivalent to the height of drop of automobile, the height of drop that is to say automobile front axle or back axle should select to make it to be equivalent to the clean deflection (distance between wheel shaft and the fixed stop absorber) of spring basically, but can not surpass it.The clean deflection of spring can be determined in advance according to the structure of automobile.
2. the speed of removing of positioning supporting frame should equal tested automotive wheel at least at gravity and in the falling speed under the effect of loose spring just between wheel and the vehicle body.Then can omit as for the friction force of vibration damper and various opposite direction effects (for example the friction force in axle oscillating bearing and the spring etc.).
3. the measurement wheel acts on the pressure transformation period course on the base.
In this method, the 2nd step of being narrated has huge especially importance for the correctness of the measurement result that obtains.In case positioning supporting frame draws below automobile, the various elastic forces in the automobile just can freely be put to good use, refer to here: when automobile is placed on the positioning supporting frame, because of the vehicle body and the spring between the wheel of the weight pressurized of automobile can be relaxed.Meanwhile, the acceleration of gravity has determined the falling speed of wheel.In addition, because that the quality of wheel is compared with vehicle body is very little, so the relaxing of spring effect almost all is reflected on the wheel, thereby gives additional acceleration of wheel again.Certainly, the size of coriolis acceleration also depends on the state in vibration damper and axle joint.Because the existence of coriolis acceleration, make the movement velocity of wheel greater than the speed of vehicle body, therefore, before body quality participated in vibration, wheel just bumped against with base and base is passed in their vibration.
Because the release of elastic force also acts on the wheel, the wheel falling speed is greater than the falling speed of vehicle body, so the distance between wheel and the vehicle body can change.On all automobiles, all used the vibration displacement of rubber fixed stop absorber to prevent that wheel is excessive.If falling faster than vehicle body, wheel bumped against with the rubber fixed stop absorber earlier before knocking base, so, the rubber fixed stop absorber is applied to the vibration characteristics that rightabout power will influence the loose spring between the vibration characteristics of wheel and vehicle body, the wheel, and the vibration that obtains will reflect the incorrect information of automobile vibration or vibration damper effect.In addition, if the situation of axletree bump rubber fixed stop absorber has taken place, then pass to a part of energy of wheel even before wheel knocks base, just be dissipated totally and the relaxing of spring amount will not reach its total kilometres by spring.
Vehicle shock absorber is that be used for the decaying vibration of spring promptly consumes the energy of spring, when the vibration characteristics of evaluation automobile, this will cause the conclusion of a mistake: think that all vibration dampers on the automobile (oscillating movement of the spring that is used to decay and consume the energy of spring) are suitable for using.
In order to prevent that wheel from contacting axletree and fixed stop absorber collision before with base, should select the height of drop of automobile modestly, that is to say, the distance between positioning supporting frame and the base, should not surpass certain maximal value, promptly be no more than the value of so-called clean spring deflection.
This value is determined according to experiment with by the structural condition that the Railway Car Plant provides.Therefore, if the driver not in car, so for any automobile, the clean deflection of this so-called spring should be 50mm at least.If the driver is in car, because the weight of having added the driver, the clean deflection of spring will increase, and also elongated to the distance of fixed stop absorber.For this reason, a safety margin can be proposed, with avoid wheel and axletree before base contacts earlier with the fixed stop absorber bump.
If in using this method, adhered to above-described principle, act on pressure measurements on the base according to wheel so, by suitable tracing analysis, under the situation of each element that need not to dismantle automobile, can obtain following result:
1. determine that automobile is independent suspension or rigid axle suspension;
2. determine the weight ratio of wheel and vehicle body;
3. the elastic property (flat tire, tire pressure) of tire is described;
4. determine the damping characteristic in axle joint;
5. the quality of vibration damper is described;
6. explanation ride performance;
7. the rigidity of travelling of automobile is described;
8. the extension and compression property ratio of explanation vibration damper;
9. the load weight of automobile is described;
10. the jammed vibration damper that may exist is described.
Be applicable to that the device of implementing the method for the invention has been equipped with a movably automobile bracing frame that is placed in the base top, the feature of this device is: base is built with the form of measuring bridge, can detect the weight of automobile and wheel and act on pressure time course on the base.In addition, the automobile bracing frame is to the distance of base, and maximum can reach the clean deflection of pre-determined motor spring.
According to the characteristics described in the dependent claims, and, the details of this device can be described more fully with reference to the explanation of synoptic diagram to a concrete device.Specific as follows:
Fig. 1 is the chassis structure synoptic diagram;
Fig. 2 measures the bridge schematic side view;
Fig. 3 has represented to measure among Fig. 2 the resiliency supported of bridge;
Fig. 4 is a mass M
2Wheel and mass M
1Vehicle body at automobile their distances of being experienced of beginning back curve over time that falls;
Fig. 5 shown automobile fall during stress (expansion force/force of compression) the time dependent block diagram of vibration damper;
Fig. 6 a has shown the oscillating curve that acts on the general pressure on the base behind the hard suspension automobile impacting base.
Fig. 6 b has shown the general pressure oscillating curve that acts on behind the soft spring suspension vehicle bump base on the base.
In the various automobiles of communications and transportation at present, independent suspension is the most common, therefore can be reduced to model shown in Figure 1 to an automobile.This simplified model can be explained method of the present invention better.
The body of a motor car 1 that partly shows among Fig. 2, its quality M
1Expression, quality is M
1Vehicle body be C by an elastic force
1Spring 2 be M with quality
2A wheel 3 connect.The elastic force C of the wheel of determining by tire pressure and type itself
2 Expression.Spring 2 and mass M
2Vibration decay by vibration damper 4 the damping force mass M of vibration damper 4
1And M
2Between damping D
2Be illustrated in Fig. 1, D
2Be parallel to elastic force C
1In the independent suspension shown in this example, spring 2 and mass M
2Vibration also decayed in addition by the friction force in wheel shaft 6 upper joints 5, also the friction force that is converted to heat by spring 2 in motion process decays, this partly damping force in Fig. 1, use D
1Expression, same, also be parallel to elastic force C
1On.
With numeral 1 to the 6 independent suspension automobile of representing, its wheel 3 is placed on the positioning supporting frame above the ramp 11 among Fig. 2 and Fig. 3, and other wheel does not show among the figure too.In measuring process, two wheels fall simultaneously to their measuring mechanism, and two wheels then rest on their base in addition.The effect of positioning supporting frame nationality hydraulic jack 12 remains on the height of sliding platform 11 and by tensioning mechanism 14 and is connected with base 7, and sliding platform 11 exceeds 50mm approximately than measuring equipment 13.In case the power of hydraulic jack 12 is interrupted, tensioning mechanism 14 just pulls off positioning supporting frame 10 under automobile.The size of positioning supporting frame 10 is bigger than the Outside Dimensions of measuring mechanism 13, so they can cross and move on the position that is lower than measuring mechanism 13, and is not in contact with it.In order to prevent positioning supporting frame 10 reverse resiliences, thereby the wheel 3 on the bump measuring mechanism 13 is distorted measurement results, and positioning supporting frame 10 can be braked mechanism 23 and tangle.In this structure, arrestment mechanism 23 is made of a hydraulic jack, the mechanism that can certainly select for use other to be suitable for.
Each measuring mechanism 13 comprises a weight plate 15, and weight plate to be measuring the arranged in form of bridge, and the crooked dynamometry beam 16 in the L shaped cross section by being configured in both sides is rigidly connected with framework 17.Two foil gauges 18 are placed in respectively on each dynamometry beam along the line of symmetry of crooked dynamometry beam.The result that foil gauge picks up utilizes a recording unit (not shown) to reproduce out with the form of curve.This curve has provided the information of the Changing Pattern of the power on the weighing plate 15 of wheel effect.In addition, the measurement result of foil gauge 18 can be input to simultaneously one suitably sequencing computing machine, computing machine compares these actual measured value and the expectation value calculated, to estimate the quality of vehicle part.
The two ends of framework 17 are placed on the roller 20 on the base plate 21, so that can move in the horizontal direction.As can be seen from Figure 3, measuring mechanism 13 is placed on the spring 22, and spring 22 can vibrate when being subjected to encouraging.
When sliding platform 11 driven by automobile, when wheel 3 was parked on the positioning supporting frame 10, automobile exceeds measured bridge 13 about 50mm.In process of the test, the driver can be sitting in the automobile, so that make test findings meet the characteristic of the automobile of travels down as much as possible.In a single day positioning supporting frame 10 is left behind, the rule that automobile is promptly pressed freely falling body falls.Lower support disappearance owing to the wheel 3 on the axletree, originally acted on tare on the wheel and removed influence too wheel, the bearing spring 2 of wheel 3 begins to relax, and wheel 3 is a radius with the length of axle 6 just, does garden arc motion around axle joint 5.Wheel 3 has departed from the upright position to be swung inwards, and hits on the weight plate 15 of measuring bridge 13 with the position of an inclination.This position of wheel and the wheel state when actual motion is not consistent, therefore, can distort test findings equally.For vibration damper, situation is all the more so, because the inclination of wheel position will make vibration damper freely not vibrate, even can produce clamping stagnation to a certain degree.For this reason, test findings will reflect the resistance of vibration damper mistakenly, and people are misunderstood to vibration damper.
In order to reach the effect when wheel 3 is in vertical position in process of the test, and vehicle body 1 can be measured bridge 13 and be mounted on the roller 20 freely to the whereabouts according to the state of actual motion, it just can be displaced sideways on base plate 21 like this.Under the effect of the relaxation force of spring 2, when wheel 3 impinged upon on the weighing plate 15 with the speed that is higher than vehicle body 1, it was be in an inclination locational that wheel 3 begins.Yet vehicle body 1 this heavier quality is when falling after the wheel, and wheel erects again, and laterally outwardly promotes weighing plate 15, makes the tire 3 can be attached on the weighing plate 15.Because the vibration of vehicle body 1, cause that wheel 3 tilts repeatedly and reforms, therefore, weighing plate 15 has just participated in this oscillating movement, utilizes this vibration information.The suspension that can judge tested automobile is independent suspension or whole bridge-type suspension.Because except that some cross-country vehicles, nearly all automobile all has independent suspension structure at present, therefore, it is an essential design feature in the measuring mechanism that the roller of weighing plate 15 supports, and it has avoided the mistake of the measurement result that causes because of the vibration damper clamping stagnation.The vibration damper catching phenomenon be to be delivered to remake on the joint 5 and to be used on the vibration damper 4 by being attached to tire 3 on the weighing plate 15.
The structure of measuring mechanism 13 should make wheel 3 when free-falling, and the drop point on weight plate is in insignificant status.This characteristic of measuring mechanism 13 is necessary for the automobile of the different wheelspans of research with the automobile that has different vehicles to depart from during free-falling.In order to accomplish this point, weight plate 15 is supported on the framework 17 by crooked dynamometry beam 16.In case automobile drops on the weight plate 15, its general assembly (TW), i.e. M
1+ M
2And the time that acts on the wheel pressure on the weight plate 15 change and can utilize foil gauge 18, obtain according to so-called differential method.
In order to estimate measurement result, must be noted that situation about being occurred in the automobile dropping process.
In bindiny mechanism, the mechanism that makes a pair of wheel of automobile begin to fall has tangible importance.During beginning, automobile is parked on the positioning supporting frame 10, and positioning supporting frame is connected with base by tension spring 14 and is lifted by hydraulic jack 12, remains on the position that exceeds measuring mechanism 13.In order to make automotive wheel 3 in the free-falling process, clash into weight plate 15, be not subjected to the adverse effect of outside various power, so under the possible situation, positioning supporting frame 10 must be to draw back from automobile lower to the bigger speed of the falling speed of weight plate 15 than wheel 3.Take place loose because the very strong spring 2 that is compressed by the weight of automobile during beginning is removed the back in support 10, wheel just has been subjected to a very large thrust, this power appends on the gravity of wheel 3, makes the speed of the speed of wheel 3 greater than freely falling body, also greater than the mass M of vehicle body 1
1Speed.When wheel contacts with weight plate 15, by the vibration characteristics of himself, at spring 2, vibration damper 4, axle oscillating bearing damping D
1Under the influence of friction force in the spring 2, wheel passes to the pressure of 15 1 variations of weight plate, and this pressure is just noted with a vibration signal by foil gauge 18.When bindiny mechanism is discussed, should be with reference to the curve among Fig. 6 a that discusses below and the 6b.
In order to remove positioning supporting frame 10 fast enough downwards, the tension spring 14 that it and rigidity is suitable is connected, and in addition, braking equipment 23 is used to the resilience of the positioning supporting frame 10 that prevents to fall.
The front points out that the accelerating effect meeting of 2 pairs of wheels 3 of spring is hindered by vibration damper 4, that is to say, the effect of vibration damper 4 is that the Conversion of energy of spring 2 is heat, and this is provided with the purpose of vibration damper just.Now, the purpose of test is to determine whether vibration damper can also finish this task fully.If following situation, promptly spring 2 only causes the as far as possible little distortion of wheel 3 when loose, can think that then vibration damper 14 is satisfied.
The friction force that produces at 5 places, axle joint will strengthen the damping action of vibration damper 4, in the ordinary course of things, these friction force are smaller, compare with the power of vibration damper, they can neglect, still, when producing these friction force when axle joint generation clamping stagnation, they just can not ignore, and after the damage of having an accident property, this situation will occur.Because these friction force are identical with the effect of vibration damper 4 to the effect of spring 2, therefore, the evaluation that the vibration damper quality is done will be distorted.
Yet expert but can be from the shape of the measurement curve of gained, makes some conclusions and can be according to these curves, the power of dissection on spring 2.
Fig. 6 a and Fig. 6 b have reproduced the time of vibration characteristic of weight plate 15.This is that sliding platform 11 driven by automobile, and positioning supporting frame 10 draws back from the below of wheel 3, takes place after automobile is fallen on the weight plate 15.In fact, these curve representations is to drop on the automobile of beating on the weight plate 15 to be applied to time dependent pressure on the weight plate 15.
This pressure is consistent with the pressure of wheel, two elastic force C that are connected in series
1With elastic force C
2Be applied to vertically downward on the wheel 3, and pass to weight plate.During this period, elastic force C
1And C
2By the mass M of free-falling
1And M
2Power encourage, cause vibration, and this vibration mentioned by the front damping force D
1And D
2Influence.Therefore, according to mass M
1And M
2Given value and the tire elastic force C of regulation
2, utilize the pressure measurements on the weight plate 15, just can obtain some relevant C of damping spring system
1, D
1, D
2The conclusion of state.This means according to the shape of measuring curve, can evaluate the spring system of hard spring and hard vibration damper, perhaps whether the spring system of soft spring and soft vibration damper has problems.
Shown in Fig. 6 b is the pressure curve of a typical soft spring system, and shown in Fig. 6 a is the pressure curve of a typical hard spring system.
Certainly, for the state of each element that will obtain automobile (as elastic force C
2, resistance of shock absorber D
2With axle joint 5 etc.) detailed conclusion, also need to analyze meticulously these and measure curve.
Because the measurement curve is a resultant curve in all cases, so curve is the superposition of various vibrations.In order to estimate measurement result, need at first consider usually resultant curve by which independently oscillating curve be formed by stacking, also should consider these independently the variation of oscillating curve be the governing factor that how to depend on them.Research will be from piece-rate system M
2, C
2With the M of system
1, C
1, D
1, D
2Vibration characteristics set about so that can evaluate the conspiracy relation of these 2 systems.
At the beginning of automobile free-falling campaign, elastic force C
2And C
1Just begin loose since loose in elastic force C
1To mass M
2Work has increased mass M in order to a downward power
2The whereabouts acceleration.Therefore, mass M
2The speed that falls is just than the mass M of only bearing action of gravity basically
1Falling speed big.Mass M
2The size of the kinetic energy during bump weight plate 15 has reflected M
2Suffered system C during falling
1, D
1, D
2The accelerating force effect, the size of this kinetic energy is to estimate vibration damper D
2A criterion of quality.If resistance of shock absorber D
2To elastic force C
1Influence very little, elastic force C
1Just loose easily, to mass M
2The acceleration that produces is just very big.Fall to moving once beginning, the very fast bump that 3 pairs of weight plate 15 of wheel just can take place, impact will be very big, and the beginning of oscillating curve partly will be near the initial point of coordinate system.
But, after the wheel 3 bump weight plate 15, the mass M that tire is acutely quickened again
2Compress, that is to say, the expression tire itself elastic force C
2Elastic deformation increase is arranged again, the increase of this repetition of elastic deformation and reducing has just formed elastic force C
2Vibration.
If elastic force C
1In dropping process, can take place loose significantly, the C of system then
1, D
2It is softer elastic oscillating system.Therefore, even wheel clashes into elastic force C later on
2Lax once more, elastic force C
1Can not be to elastic force C
2Produce how many resistances.So, vibration incipient stage, elastic force C
2Obstruction suffered in vibration is just smaller.And the C of system
1, D
2Bear the stretching and the force of compression that alternately occur.
System M
2, C
2Though be subjected to the M of system
1, C
1, D
2Influence (damping D
1Produce by the axle joint,, omitted because very little), but owing to have internal damping, so the energy of vibration of this system comparatively fast disappears.
Mass M
2And M
1Zhen Dong time is very short simultaneously, and during this period of time, vibration damper 4 is alternately stretched and compresses.Find out this of short duration alternating tensile/compression process of vibration damper 4 block diagram can be below Fig. 4 shown in Figure 5.Related zone is distinguished with hacures.
Till wheel 3 bump weight plate 15, elastic force C
1Relaxing vibration damper D always
2Only be subjected to stretching action.Variation has taken place in these situations after wheel 3 bump weight plate.Elastic force C
1The mass M of being quickened to fall
1Effect be compressed, therefore, after transient oscillation compression/draw stage disappeared, vibration damper is only effect by compression just.This vibration processes is corresponding to " subordinate phase " time interval in the curve of Fig. 6 a and Fig. 6 b.
If the curve of " subordinate phase " among Fig. 6 a and the 6b and figure shown in Figure 4 cooperated see, just be more readily understood these curves.In Fig. 4, mass M
1And M
2Residing position in vibration processes can illustrate on schedule.Datum line is taken as the normal position of this quality wheel and vehicle body.Mass M
2To be higher than M
1The speed free-falling, this stage till wheel 3 knocks weight plate 15, can be from M
2Curve is seen (dot-and-dash line).After wheel 3 collisions, tire is compressed, and that is to say mass M at a high speed
2Compressed elastic force C
2So, mass M
2Be on the position that is lower than datum line, that is be lower than its normal position.
Mass M
1Motion represent that with solid line the beginning of curve is partly corresponding to free-falling, after wheel 3 bumped, quality was M
1Vehicle body 1 because of being subjected to loose elastic force C
1The effect that makes progress, its free-falling speed has minimizing slightly.However, because mass M
1The kinetic energy of itself, its remaining acceleration still is enough to make mass M
1Below datum line, move, at this moment spring C
1Be compressed mass M
1Recurrent point in datum line bottom, in this point place, mass M
1Kinetic energy exhaust and elastic force C
1Middle energy stored reaches its maximum value.Then, by mass M
1The elastic force C of compression
1Loose, and upwards promote mass M
1Above-mentioned vibration processes will repeat, and this depends on C
1, D
1, D
2The elastic force intensity of system, and this process always stops sooner or later.The same with spring 2, vibration damper 4 also alternately is stretched or compressed, up to mass M
1And M
2Motion stop, getting back to (consulting block diagram 5) till their the normal zero position.
Understand the motion of the curve among Fig. 4, acted on subordinate phase pressure Changing Pattern on the weight plate 15 with regard to easy to understand shown in Fig. 6 a and the 6b.
In subordinate phase, by mass M
1The spring power C that is compressed
1Begin again to relax mass M
1Be pushed upwardly, pressure reduces.For hard suspension C
1, D
1, elastic force C
1loosely finish very soon, this means that suppressed range will be below horizontal dotted line.Horizontal dotted line is represented the datum pressure by the actual weight of automobile (static weight) generation.Therefore, being applied to pressure on the weight plate 15 is less than the static weight of the automobile on weight plate 15.
According to mass M shown in Figure 4
1And M
2The motion of curve, their action is how to influence the pressure Changing Pattern shown in Fig. 6 a and the 6b in the transient oscillation phase one as can be seen.That section curve that dots among Fig. 6 a and the 6b can be regarded fundamental vibration as, can be according to mass M shown in Figure 4
1Vibration characteristics push away.
First peaked height can be used as vibrational system C on the steepness of the curve that dotted line is represented among Fig. 6 a and the 6b and the curve
1, M
1, D
2In a tolerance of mutual relationship between each power.
The phase one curve that solid line is represented among Fig. 6 a and the 6b is a summation curve, and it is corresponding to the elastic property and the M of system of tire
2, C
2Vibration characteristics.
For soft suspension system that is soft elastic force C
1With soft vibration damper 4, elastic force C described above
2Vibration characteristics can at first be obtained.(Fig. 6 b) is longer for the rising edge of fundamental vibration curve, and not really steep.Fig. 6 b(soft spring system) shown in curve and Fig. 6 a(hard spring system) shown in curve compare, can find out that first vibration amplitude is more flat, first vibration maximal value occurs relatively late.
For the C of hard spring system
1, D
2, because hard elastics power C
1Can stop elastic force C
2Complex vibration, therefore, it is repressed that transient oscillation is actually.Because quality is M
2Wheel 3 be not subjected to lax elastic force C
1Very big acceleration, so the beginning of vibration is later than soft suspension system slightly, the rising of curve is steeper, first amplitude is higher and just reach in a short period of time.
According to first part of curve, can get following conclusion: the fundamental curve of soft suspension rises lentamente, illustrates that ride performance is good; The precipitous rising of fundamental curve of hard suspension illustrates that ride performance is relatively poor.
The elastic property of wheel 3, in the phase one pressure curve be superposition on the fundamental vibration of vehicle body 1, therefore,, just can obtain the conclusion of the quality of vibration damper 4 according to the pressure curve of phase one.
Therefore, use above-mentioned measuring system,, just may from total vibration characteristics of automobile, extract the characteristic of vibration damper, can clearly describe the quality of vibration damper and need not it is unloaded by analyzing the pressure on the weight plate 15.
According to all being known data M concerning each automobile
1, M
2, C
1, C
2, can calculate the theoretical oscillating curve of automobile, and it can be compared with actual measurement curve.
Certainly, when practical application, the necessary data of those theoretical curves, can import robot calculator, computing machine can compare empirical curve and theoretical curves pointwise, and according to the program of input, computing machine will provide the report of sub-standard various defectives.
Claims (13)
1, a kind of method that is used to detect the state of automobile chassis.Automobile is placed on the positioning supporting frame of base top, removes positioning supporting frame then, automobile is fallen, the automobile front axle and the back axle of free-falling just fall to base.This method is characterised in that:
(1) distance between positioning supporting frame and the base is equivalent to the height of drop of automobile, and the selection of this distance should be suitable with the clean deflection of spring (distance between wheel shaft and the fixed stop absorber) basically, can not surpass it.The clean deflection of spring can pre-determine according to the structure of automobile.
(2) speed of removing positioning supporting frame should equal the falling speed of tested automotive wheel at least, and the wheel of whereabouts just is subjected between gravity and wheel and the vehicle body effect at loose spring.Friction force (for example friction force in axle joint and the spring) as for vibration damper and various opposite direction effects then can be omitted.
(3) measurement acts on the time history that the wheel pressure on the base changes.
2, by the described method of claim 1, it is characterized in that: for the independent suspension vehicle, as can be known the vibration characteristics and the vibration characteristics of vehicle body and impinge upon wheel on the base in advance by suspension system can make base move in the horizontal direction.
3, by claim 1 or 2 described methods, it is characterized in that: the distance between positioning supporting frame and the base is 10mm to 60mm, preferably 50mm.
4, by described method one of in the claim 1 to 3, it is characterized in that: the bump of wheel can cause the vibration of base.
5, device of one of implementing in the claim 1 to 4 described method, comprise an automobile bracing frame that movably is placed in the base top, it is characterized in that: base (15) is by the form design of measuring bridge (13), and weight and wheel that base can measured automobiles act on the time history that the pressure on the base changes.Distance between automobile bracing frame (10) and the base (15) can only equal the clean deflection of predetermined motor spring at most.
6, by the described device of claim 5, it is characterized in that: measure bridge (13) and be by the form design of static weighing machine, it can weigh up the weight of automobile and not be subjected to the influence of the drop point site of wheel (3) on base (15), measures bridge (13) and also comprises a mechanism that measures the time history that applied pressure changes.
7, by the described device of claim 6, it is characterized in that: pressure is measured with foil gauge (18).
8, by described device one of in the claim 5 to 7, it is characterized in that: measure bridge (13) and be placed on the base plate (17), can on the base bridge, move by along continuous straight runs, at least can be to moving on one side.
9, by described device one of in the claim 5 to 8, it is characterized in that: automobile bracing frame (10) links to each other with a spring element (14) that gives stretching, after the automobile bracing frame unclamps, this spring element draws back the automobile bracing frame with the speed identical with the falling speed of wheel (13) at least below wheel, the speed of drawing back preferably can be greater than the falling speed of wheel.
10, by described device one of in the claim 5 to 9, it is characterized in that: the size that has a breach, the size of breach to be slightly larger than to be placed in the measurement bridge (13) below the breach on the automobile bracing frame (10).
11, by described device one of in the claim 5 to 10, it is characterized in that: measuring bridge (13) is (being installed on the parts 22) of flexibly installing.
12, by described device one of in the claim 5 to 11, it is characterized in that: measure the vibration that bridge (13) energy measurement frequency reaches 1KHz at least.
13, by described device one of in the claim 5 to 12, it is characterized in that: the arrestment mechanism (23) of a bus location bracing frame (10) is provided, and in that to remove pin fixed, after the automobile bracing frame was removed under the wheel, it can prevent the resilience of automobile bracing frame.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19853545087 DE3545087A1 (en) | 1985-12-19 | 1985-12-19 | METHOD AND DEVICE FOR CHECKING THE CHASSIS OF A MOTOR VEHICLE |
| DEP3545087.8 | 1985-12-19 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN86108430A true CN86108430A (en) | 1987-07-01 |
Family
ID=6288944
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN198686108430A Pending CN86108430A (en) | 1985-12-19 | 1986-12-19 | The method and apparatus that is used for testing vehicles |
Country Status (7)
| Country | Link |
|---|---|
| US (1) | US4761991A (en) |
| EP (1) | EP0226981B1 (en) |
| JP (1) | JPS62156536A (en) |
| CN (1) | CN86108430A (en) |
| AT (1) | ATE50639T1 (en) |
| CA (1) | CA1294795C (en) |
| DE (2) | DE3545087A1 (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1314951C (en) * | 2004-05-10 | 2007-05-09 | 林武 | Chassis test bench for cars |
| CN101813514A (en) * | 2010-03-12 | 2010-08-25 | 重庆长安汽车股份有限公司 | Mobile automobile body modal test bed |
| CN101929854A (en) * | 2010-08-15 | 2010-12-29 | 吉林大学 | 3-freedom-degree wheel clearance detection platform |
| CN101943635A (en) * | 2010-09-05 | 2011-01-12 | 荆门宏图特种飞行器制造有限公司 | Damping spring test device for motor vehicle |
| CN102192842A (en) * | 2011-03-25 | 2011-09-21 | 唐光涛 | Abnormal sound diagnostic instrument of automobile body chassis |
| CN102565869A (en) * | 2011-12-30 | 2012-07-11 | 洛阳圣瑞机电技术有限公司 | Mobile safety inspection device of automobile chassis |
| CN102589859A (en) * | 2011-12-14 | 2012-07-18 | 北京理工大学 | Fatigue testing system for outer connection sleeve of suspension frame strut assembly |
| CN104931272A (en) * | 2015-05-15 | 2015-09-23 | 澳门大学 | Novel high-precision road simulation test platform for quarter vehicle model |
| CN105527065A (en) * | 2015-11-26 | 2016-04-27 | 安徽江淮汽车股份有限公司 | Impact test device for wheel casing |
| CN106662503A (en) * | 2014-05-28 | 2017-05-10 | 株式会社昭和 | Method and system for inspecting damping force variable mechanism, and method for inspecting pressure damping device |
| CN107917662A (en) * | 2017-12-29 | 2018-04-17 | 浙江众泰汽车制造有限公司 | Vehicle bumper block strain detection testing device |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB8815167D0 (en) * | 1988-06-25 | 1988-08-03 | Liquid Levers Ltd | Method & apparatus for testing shock absorbers &/suspension systems in or on motor vehicles |
| US5767382A (en) * | 1988-06-25 | 1998-06-16 | Liquid Levers Limited | Method and apparatus for testing shock absorbers and/or suspension system in motor vehicles |
| US5191783A (en) * | 1991-04-25 | 1993-03-09 | Abbott W Bruce | Portable basketball rim testing device |
| US5214954A (en) * | 1992-01-21 | 1993-06-01 | Abbott W Bruce | Portable basketball rim testing device |
| DE4431794A1 (en) * | 1994-09-06 | 1996-03-07 | Langlechner Richard Gmbh | Method and device for determining the properties of shock absorbers installed in a motor vehicle |
| EP0962758A3 (en) * | 1998-05-08 | 2000-04-26 | Beissbarth GmbH | Device for determining the conditions of a wheel suspension of a vehicle |
| DE10029282A1 (en) * | 2000-06-14 | 2001-12-20 | Bosch Gmbh Robert | Loading state determining method for vehicle, involves detecting temporal change of measured tire pressure |
| GB0609049D0 (en) * | 2006-05-08 | 2006-06-14 | Airbus Uk Ltd | Method and apparatus for applying bending load to an axle of an aircraft landing gear |
| US7946163B2 (en) | 2007-04-02 | 2011-05-24 | Penske Racing Shocks | Methods and apparatus for developing a vehicle suspension |
| US7786850B1 (en) * | 2008-06-16 | 2010-08-31 | Gianni Arcaini | Method and apparatus for bridge collision alert monitoring and impact analysis |
| CN101526426B (en) * | 2009-04-27 | 2011-02-16 | 西南交通大学 | Method for wirelessly testing dynamic performance of oscillating damper for train and device thereof |
| JP5836054B2 (en) * | 2011-10-25 | 2015-12-24 | 株式会社ブリヂストン | Tire test method |
| CN104048823B (en) * | 2014-07-09 | 2016-08-24 | 上海理工大学 | Variation rigidity virtual automobile body clamp suspension testing stand |
| US9863839B2 (en) * | 2015-11-18 | 2018-01-09 | The Boeing Company | Positioner for electrodynamic shaker |
| RU197377U1 (en) * | 2020-01-31 | 2020-04-23 | Андрей Владимирович Донцов | TEST STAND FOR RESEARCH OF INFLUENCE OF MEANS OF MECHANICAL TRAILING OF MINO EXPLOSIVE DAMAGES ON WHEEL MACHINES |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3164003A (en) * | 1960-02-19 | 1965-01-05 | Bear Mfg Co | Portable shock absorber tester |
| US3157044A (en) * | 1961-11-24 | 1964-11-17 | Branick Mfg Co | Shock absorber testing and condition indicating device |
| US3456489A (en) * | 1968-01-16 | 1969-07-22 | Sol J Levenson | Shock absorber tester |
| ZA706176B (en) * | 1969-11-13 | 1971-05-27 | Monroe Belgium Nv | Shock absorber testing apparatus |
| SE377497B (en) * | 1973-01-17 | 1975-07-07 | R P S Graham | |
| DE2332349A1 (en) * | 1973-06-26 | 1975-01-16 | Volkswagenwerk Ag | Motor car shock absorber test rig - has raisable plates with strain gauges for each car wheel |
| DE2334737A1 (en) * | 1973-07-09 | 1975-04-03 | Volkswagenwerk Ag | PROCEDURE FOR TESTING THE WORKABILITY OF SHOCK ABSORBERS |
| DE2335886A1 (en) * | 1973-07-14 | 1975-01-30 | Volkswagenwerk Ag | Motor vehicle shock absorber testing device - device drops wheel to produce oscillations of vehicle |
-
1985
- 1985-12-19 DE DE19853545087 patent/DE3545087A1/en active Granted
-
1986
- 1986-12-12 DE DE8686117356T patent/DE3669205D1/en not_active Expired - Lifetime
- 1986-12-12 EP EP86117356A patent/EP0226981B1/en not_active Expired - Lifetime
- 1986-12-12 AT AT86117356T patent/ATE50639T1/en not_active IP Right Cessation
- 1986-12-18 CA CA000525679A patent/CA1294795C/en not_active Expired - Lifetime
- 1986-12-19 JP JP61301874A patent/JPS62156536A/en active Granted
- 1986-12-19 CN CN198686108430A patent/CN86108430A/en active Pending
- 1986-12-19 US US06/943,754 patent/US4761991A/en not_active Expired - Lifetime
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1314951C (en) * | 2004-05-10 | 2007-05-09 | 林武 | Chassis test bench for cars |
| CN101813514A (en) * | 2010-03-12 | 2010-08-25 | 重庆长安汽车股份有限公司 | Mobile automobile body modal test bed |
| CN101813514B (en) * | 2010-03-12 | 2011-11-09 | 重庆长安汽车股份有限公司 | Mobile automobile body modal test bed |
| CN101929854B (en) * | 2010-08-15 | 2012-08-08 | 吉林大学 | 3-freedom-degree wheel clearance detection platform |
| CN101929854A (en) * | 2010-08-15 | 2010-12-29 | 吉林大学 | 3-freedom-degree wheel clearance detection platform |
| CN101943635A (en) * | 2010-09-05 | 2011-01-12 | 荆门宏图特种飞行器制造有限公司 | Damping spring test device for motor vehicle |
| CN102192842A (en) * | 2011-03-25 | 2011-09-21 | 唐光涛 | Abnormal sound diagnostic instrument of automobile body chassis |
| CN102192842B (en) * | 2011-03-25 | 2013-08-21 | 唐光涛 | Abnormal sound diagnostic instrument of automobile body chassis |
| CN102589859A (en) * | 2011-12-14 | 2012-07-18 | 北京理工大学 | Fatigue testing system for outer connection sleeve of suspension frame strut assembly |
| CN102589859B (en) * | 2011-12-14 | 2014-10-08 | 北京理工大学 | Fatigue testing system for outer connection sleeve of suspension frame strut assembly |
| CN102565869A (en) * | 2011-12-30 | 2012-07-11 | 洛阳圣瑞机电技术有限公司 | Mobile safety inspection device of automobile chassis |
| CN106662503A (en) * | 2014-05-28 | 2017-05-10 | 株式会社昭和 | Method and system for inspecting damping force variable mechanism, and method for inspecting pressure damping device |
| US10564071B2 (en) | 2014-05-28 | 2020-02-18 | Showa Corporation | Method and system for inspecting damping force variable mechanism, and method for inspecting pressure damping device |
| CN106662503B (en) * | 2014-05-28 | 2020-03-31 | 株式会社昭和 | Method and system for inspecting damping force variable mechanism and method for inspecting pressure damping device |
| CN104931272A (en) * | 2015-05-15 | 2015-09-23 | 澳门大学 | Novel high-precision road simulation test platform for quarter vehicle model |
| CN105527065A (en) * | 2015-11-26 | 2016-04-27 | 安徽江淮汽车股份有限公司 | Impact test device for wheel casing |
| CN105527065B (en) * | 2015-11-26 | 2018-05-04 | 安徽江淮汽车集团股份有限公司 | The impact test apparatus of wheel cover |
| CN107917662A (en) * | 2017-12-29 | 2018-04-17 | 浙江众泰汽车制造有限公司 | Vehicle bumper block strain detection testing device |
Also Published As
| Publication number | Publication date |
|---|---|
| US4761991A (en) | 1988-08-09 |
| EP0226981A3 (en) | 1988-06-01 |
| EP0226981A2 (en) | 1987-07-01 |
| DE3545087A1 (en) | 1987-07-02 |
| EP0226981B1 (en) | 1990-02-28 |
| JPH0562940B2 (en) | 1993-09-09 |
| DE3545087C2 (en) | 1988-06-30 |
| JPS62156536A (en) | 1987-07-11 |
| ATE50639T1 (en) | 1990-03-15 |
| DE3669205D1 (en) | 1990-04-05 |
| CA1294795C (en) | 1992-01-28 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN86108430A (en) | The method and apparatus that is used for testing vehicles | |
| US6161419A (en) | Process and device for determining the characteristics of a motor ' vehicles built-in shock-absorbers | |
| CN105784347B (en) | A kind of helical spring dynamical property test system and test method | |
| CN205209792U (en) | Proportion automobile body fatigue strength and loading spectrum research test platform under multiple spot excitation load | |
| CN108482420A (en) | Rail traffic rail system wheel track coupling dynamic characteristic test method | |
| CN101556204A (en) | Impact test method for restoration characteristics of motorcycle front suspension | |
| CN108414178B (en) | Impact device with buffering function and application method thereof | |
| CN113465943A (en) | Automobile subsystem collision test device and method | |
| Fermér et al. | Wheel/rail contact forces for flexible versus solid wheels due to tread irregularities | |
| CN214309523U (en) | Vehicle suspension detection equipment | |
| US4589273A (en) | Method of testing shock absorption of a spring running gear, particularly undercarriage of a road motor vehicle with elastic tires and apparatus for performing the method | |
| Vrtanoski et al. | Dynamic testing of innovative railway brake system for freight wagons | |
| CN116499727A (en) | Detection device and detection control method for high-speed train windscreen wiper | |
| CN214040570U (en) | Device for high-acceleration collision impact test | |
| EP3256830A2 (en) | Multi -plate apparatus and method for checking the braking system of land vehicles with at least two axles | |
| RU2765582C1 (en) | Test stand for pneumatic tires and elastic elements of vehicle suspenders | |
| Bosso et al. | Simulation of narrow gauge railway vehicles and experimental validation by mean of scaled tests on roller rig | |
| RU2753737C1 (en) | Universal method for vehicle reliability road tests | |
| CN206804499U (en) | A kind of device for determining surface friction coefficient | |
| Uzzal et al. | Design and Analysis of MEMS based accelerometer for automatic detection of railway wheel flat | |
| RU159632U1 (en) | DYNAMIC LOAD INSTALLATION | |
| CN112304551B (en) | Stability testing device and method for motor train unit bogie | |
| CN213632684U (en) | Device for measuring degree of throw of whole vehicle and engine after being impacted by uneven road surface | |
| RU217487U1 (en) | Loading mechanism for bench testing of pneumatic tires and elastic elements of vehicle suspensions | |
| RU2765316C1 (en) | Stand for testing pneumatic tires and elastic elements of vehicle suspensions |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |